EP1476709A1 - Heat exchanger tube with tumbling toy-shaped passages and heat exchanger using the same - Google Patents
Heat exchanger tube with tumbling toy-shaped passages and heat exchanger using the sameInfo
- Publication number
- EP1476709A1 EP1476709A1 EP02741495A EP02741495A EP1476709A1 EP 1476709 A1 EP1476709 A1 EP 1476709A1 EP 02741495 A EP02741495 A EP 02741495A EP 02741495 A EP02741495 A EP 02741495A EP 1476709 A1 EP1476709 A1 EP 1476709A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- heat exchanger
- passages
- curved portion
- thickness
- exchanger tube
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/02—Tubular elements of cross-section which is non-circular
- F28F1/04—Tubular elements of cross-section which is non-circular polygonal, e.g. rectangular
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
- F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
- F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
- F28D1/05383—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/02—Tubular elements of cross-section which is non-circular
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/02—Tubular elements of cross-section which is non-circular
- F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
- F28D2021/007—Condensers
Definitions
- the present invention relates to a heat exchanger tube with a plurality of tumbling toy-shaped passages and a heat exchanger using the heat exchanger tube.
- an air conditioning device for a vehicle includes a heat exchanger that is provided with a condenser exchanging refrigerant being at high temperature and pressure delivered from a compressor with an external air to thereby make the heat-exchanged refrigerant liquefied, and with an evaporator that enables the liquefied refrigerant to be varied into air being at a low temperature such that the air around the low temperature air becomes cool.
- Each of the condenser and evaporator includes a plurality of tubes, each of which has a plurality of refrigerant passages through which the refrigerant is passed, a plurality of corrugated fins placed between the tubes in a form of wave, a pair of header tanks that connect the both ends of each of the tubes in such a manner as to communicate with the tubes, and inlet and outlet pipes disposed in each of the header tanks, to and from which the refrigerant flows.
- the condenser of the heat exchanger as mentioned above is provided with the plurality of flat-shaped tubes, each of which has a multipassage formed therein. This is disclosed in Japanese Patent Publication No. 11-159985.
- the above-mentioned conventional heat exchanger is provided with a plurality of heat exchanger tubes 11 , each of which forms a plurality of refrigerant passages 15 or 21 therein, wherein the refrigerant passages 15 or 21 with a polygonal or circular section are connected with each other, disposed in the same direction.
- the above-discussed conventional heat exchanger has had the following problems. So as to improve the performance of the heat exchanger, typically, it is important to increase a heat transfer area where the refrigerant is heat-exchanged. To do this, there has been provided a method in which a hydraulic diameter is reduced.
- the plurality of refrigerant passages 15 or 21 are disposed in the width direction of the heat exchanger tube 11, and if the ratio of the width w of each of the refrigerant passages 15 or 21 to the height h is set higher than 1 (that is, w/h>l), a wall thickness t becomes increase as the hydraulic diameter is set relatively low in the heat exchanger provided with the heat exchanger tube 11 having the same size.
- FIG. 3 shows another conventional heat exchanger, which is disclosed in Japanese Patent Publication No. 2000-111290.
- the above-mentioned conventional heat exchanger is provided with a multipassage type of flat tube 5 in which a plurality of generally oval refrigerant passages 2a that are spaced apart equally, inclined by a predetermined angle against the direction of an axis y.
- the conventional heat exchanger as mentioned above has failed to improve the heat transfer efficiency thereof.
- the above-mentioned conventional type of the heat exchangers undesirably form a pin hole on the external side of each of the tubes such that the pin hole is not filled even in the brazing process thereof, which results in the increment of the generation of the defective heat exchanger.
- the tube should be manufactured only at the predetermined extruding speed, which of course will cause the productivity thereof to be undesirably low.
- the present invention is directed to a heat exchanger tube with a tumbling toy-shaped passage and a heat exchanger using the heat exchanger tube that substantially obviates one or more problems due to limitations and disadvantages of the related art.
- An object of the present invention is to provide a heat exchanger tube with a tumbling toy-shaped passage and a heat exchanger using the heat exchanger tube that can maintain a tube thickness at a predetermined value, even when a hydraulic diameter is set low such that a heat transfer area increases so as to improve the performance of a heat exchanger, thereby allowing the weight of the tube and the production cost thereof to be reduced, that can evenly distribute the stress caused by the operating pressure of a heat exchanging medium onto a plurality of refrigerant passages, not gathered partially on the refrigerant passages, such that a resistant pressure strength is substantially enough, thereby allowing the heat exchanging medium to be substantially replaced with carbon dioxide, that can make, in case where the tube is applied in a condenser, the film of
- a heat exchanger tube with a plurality of tumbling toy-shaped passages that has a generally flat body having predetermined values in length, height and width directions, the plurality of refrigerant passages formed passed through the interior of the flat body in the length direction thereof, the heat exchanger tube including: each of the plurality of refrigerant passages is provided with a plurality of inside passages, each of which has a first curved portion that is made by changing a predetermined curve over at least a time or more to form a curve changing point protruding in the width direction of the body by which turbulence activating parts are formed, and has a second curved portion that is formed opposite to the first curved portion and is connected slowly to the first curved portion to thereby form a curve closed face, and with a pair of outside passages disposed on the outermost both ends of the plurality of inside passages.
- a heat exchanger including: a plurality of tubes, each of which is comprised of a plurality of inside passages, each of which has a first curved portion that is made by changing a predetermined curve over at least a time or more to form a curve changing point protruding in the width direction of a body, by which turbulence activating parts are formed, and has a second curved portion that is formed opposite to the first curved portion and is connected slowly to the first curved portion to thereby form a curve closed face, and a pair of outside passages disposed on the outermost both ends of the plurality of inside passages, the plurality of tubes spaced apart equally through each of which a heat exchanging medium flows; and a pair of header tanks that are spaced apart equally in parallel relation with each other such that the both ends of each of the tubes communicate with each other, through which the heat exchanging medium flows.
- FIG.1 is a sectional view of the prior art heat exchanger tube
- FTG.2 is a sectional view of another type of the prior art heat exchanger tube
- FIG.3 is a sectional view of still another type of the prior art heat exchanger tube
- FIG. 4 is a top view of the condenser of a heat exchanger to which a heat exchanger tube according to one embodiment of the present invention is applied;
- FIG. 5 is a perspective view of the external appearance of the heat exchanger tube according to the one embodiment of the present invention
- FIG. 6 is a sectional view taken along the line "A- A" in FIG. 4;
- FIG. 7 is a sectional view of a heat exchanger tube according to another embodiment of the present invention wherein two turbulence activating parts are provided each curved portion;
- FIGS. 8 to 14 are partly sectional views of the heat exchanger tube according to another embodiment of the present invention.
- FIG. 15 is a perspective view of the external appearance of the heat exchanger to which the heat exchanger tube according to the present invention is applied, wherein a heat exchanging medium is used with carbon dioxide; and FIGS. 16 and 17 are sectional views of the embodiments of the heat exchanger tube in FIG. 15.
- the condenser 100 includes, as shown in FIG. 4, a pair of header tanks 200, each of which has a passage through which a heat exchanging medium is passed therein, a plurality of tubes 300 through each of which the heat exchanging medium flows, and a plurality of corrugated fins 400 placed between the tubes 300.
- the both ends of each of the plurality of tubes 300 are connected to the header tanks 200, and each of the header tanks 200 includes at least one or more baffles 500 therein such that it forms a plurality of passages by the plurality of tubes 300.
- the present invention is directed to the plurality of tubes 300, each of which includes a generally flat body 350, as shown in FIG. 5, that has predetermined values in length (an axis X), height (an axis Y) and width (an axis Z) directions thereof.
- the body 350 is provided with a plurality of refrigerant passages 340, each of which is passed through the interior thereof in the length direction thereof (along the axis X).
- Each of the refrigerant passages 340 includes a plurality of inside passages 320 and a pair of outside passages 330 provided on the outermost both ends of the body 350.
- each of the inside passages 320 has a first curved portion 321 that is made by changing a predetermined curve 321a over at least a time or more to form a curve changing point protruding in the width direction of the body 350, thereby forming a turbulence activating part 321b thereon, and a second curved portion 322 that is formed opposite to the first curved portion 321 in the width direction thereof and is connected slowly to the first curved portion 321 to thereby form a curve closed face.
- the second curved portion 322 is made by changing a predetermined curve 322a over at least a time or more to form a curve changing point protruding in the width direction of the body 350, thereby forming a turbulence activating part 322b thereon.
- each of the curves 321a and 322a constituting the first and second curved portions 321 and 322 is formed in the same curvature as a circle.
- each of the curves 321a and 322a constituting the first and second curved portions 321 and 322 is formed in the same curvature as an oval, as shown in FIGS. 8 and 9.
- the inside passages 320 are formed in the height direction (along the axis y) of the body 350, on condition that the ratio of the width Wl to the height HI is less than 1 (that is, W1/H1 ⁇ 1).
- the wall thickness can be maintained at a predetermined value even when a hydraulic diameter is set small so as to increase the heat transfer area for improving the performance of the heat exchanger. That is to say, the problem as arisen conventionally that the wall thickness increases as the hydraulic diameter is set small which causes the weight of the heat exchanger tubes 11 to undesirably increase and causes the consumption of the material to be made, thereby rendering the production cost become high, can be fundamentally eliminated.
- the pair of outside passages 330 are disposed on the outermost both ends of the inside passages 320, each of which includes a third curved portion 331 that is formed in such a manner that a part of the curve close to the outermost end of the body 350 has a roughly same shape as the section of the both ends of the body 350, and a fourth curved portion 332 that is formed by connecting the both end points of the third curved portion 331 to thereby form a closed curved face.
- the fourth curved portion 332 is formed in the same shape as any of the first and second curved portions 321 and 322 of each of the inside passages 320, as shown in FIGS. 6 and 7.
- the third curved portion 331 and the fourth curved portion 332 are disposed in symmetrical relation with each other and the fourth curved portion 332 is of a desirable circular arc shape.
- the fourth curved portion 332 is of a generally straight line shape, as shown in FIG. 13.
- the turbulence activating parts 321b and 322b are formed in such a manner that a plurality of imaginary lines
- the turbulence activating parts 321b and 322b are formed in such a manner that a plurality of imaginary lines 13 connecting the turbulence activating parts 321b and 322b of the plurality of inside passages 320 are alternated at a predetermined angle with the imaginary line II dividing said body 350 into two equal parts in the height direction of the body 350.
- the turbulence activating parts 321b and 322b are formed in such a manner that a plurality of imaginary lines 12 connecting the turbulence activating parts 321b and 322b of the plurality of inside passages 320 are disposed upwardly and downwardly around the imaginary line II dividing said body
- the refrigerant that is passed through the inside passages 320 are activated to be turbulent, thereby improving heat transfer performance.
- the hydraulic diameter Dh of each of the inside and outside passages 320 and 330 is equal to or larger than 0.55 mm, and smaller than or equal to 1.55 mm, which is set to satisfy the condition that 0.55 mm ⁇ Dh ⁇ 1.55 mm. Even when the above-mentioned hydraulic diameter is set, the shortest thickness tl in the height direction of the body 350 of the thickness from the inner surface of each of the inside passages 320 to the outer surface of the body 350 can be maintained constantly without any increment.
- a value that is obtained by dividing the length LI of the definite straight line, which connects the center points of the two curves adjacent among the curves 321a constituting the first curved portion 321, into a length L2 of the longest distance between the two curves is equal to or larger than 0.3, and smaller than or equal to 0.8, which is set to satisfy the condition that 0.3 ⁇ Ll L2 ⁇ 0.8.
- the reason why the above condition is satisfied is that if the longest distance value L2 is over a predetermined value, the protruding height of each of the turbulence activating parts 321b and 322b becomes high such that it is difficult to manufacture the extruding mold thereof and they are liable to be easily damaged structurally.
- the angle ⁇ that comes into contact with the curve at the apex of each of the turbulence activating parts 321b and 322b is larger than 80 ° and smaller than 160 °, which is set to satisfy the condition that 80 ° ⁇ ⁇ ⁇ 160 °.
- the shortest thickness t in the width direction of the body 350 among the thickness from the inner surface of each of the outside passages 330 to the outer surface of the body 350 should be set larger by 1.25 times than the shortest thickness tl in the height direction of the body 350 among the thickness from the inner surface of each of the inside passages 320 to the outer surface of the body 350, which is set to satisfy the condition that t > 1.25 tl.
- a shortest thickness t2 in the width direction of the body 350 among the thickness in the width direction between the inside passages 320 should be equal to or larger than 0.15mm and equal to or smaller than 0.35mm, which is set to satisfy the condition that 0.15 mm ⁇ t2 ⁇ 0.35 mm.
- the 350 of the thickness in the width direction between the inside passages 320 should be equal to or smaller than the shortest thickness t in the width direction of the body 350 of the thickness from the inner surface of each of the outside passages 330 to the outer surface of the body 350, which is set to satisfy the condition that t2 ⁇ t.
- the shortest thickness t2 in the width direction of the body 350 of the thickness in the width direction between the inside passages 320 should be equal to or smaller than the shortest thickness tl in the height direction of the body 350 of the thickness from the inner surface of each of the inside passages 320 to the outer surface of the body 350, which is set to satisfy the condition that t2 ⁇ tl.
- a Freon refrigerant has been mainly used as a heat exchanging medium that flows within the above-mentioned heat exchanger tube 300.
- the Freon refrigerant is treated as one of causes that make the earth warm, so that the control for use of it becomes gradually strengthened.
- many studies for replacing the Freon refrigerant with a carbon dioxide refrigerant as most worth noticing at next generation have been made all over the world.
- the carbon dioxide has some advantages that the operating compression ratio is low such that the volume efficiency is excellent and the heat transfer characteristic is extremely excellent such that the difference between the temperature on the inlet to which air as a secondary fluid flows and the temperature on the outlet from which refrigerant flows is relatively small when compared with the existing refrigerant. This exhibits many advantages as the refrigerant as well as exhibits a high degree of applicability to a heat pump. As described above, an explanation of the heat exchanger using the carbon dioxide 600 as a heat exchanging medium will be discussed on the basis of the flowing process of the refrigerant with reference to FIG. 16.
- the carbon dioxide flowing through an inlet 610 is moved to an internal passage 631 of a second header tank 630 from an internal passage 621 of a first header tank 620 and from a first tube 632 that is inserted into the slots (now shown) on the header tanks in such a manner as to be connected to the internal passage 631 of the second header tank 630.
- the carbon dioxide refrigerant flowing into internal passage 631 of the second header tank 630 is returned to an internal passage 631a of the second header tank 630 adjacent thereto through a return hole (which is omitted in the drawing).
- the carbon dioxide refrigerant is returned again to an internal passage 621a of the first header tank 620 from the internal passage 631a of the second header tank 630 and from a second tube 633 that is inserted into the slots (not shown) on the header tanks in such a manner as to be connected to the internal passage 621a of the first header tank 620.
- the carbon dioxide refrigerant flows to the internal passage 621a of the first header tank 620, it is thermally exchanged again with the external air through the second tube 633 and the corrugated fins 634.
- the temperature on the outlet of the carbon dioxide refrigerant is substantially close to the temperature on the inlet of the external air.
- each of the first and second tubes 632 and 633 as the components of the heat exchanger using the carbon dioxide refrigerant 600 is, as shown in FIGS. 4 to 7 and FIGS. 16 and 17, comprised of the generally flat body 350 that has predetermined values in length (an axis X), height (an axis Y) and width (an axis Z) directions.
- the refrigerant passage 340 is formed passed through the interior of the flat body 350 in the length (the axis X) direction thereof.
- the refrigerant passage 340 is provided with the plurality of inside passages 320, each of which has the first curved portion 321 that is made by changing the predetermined curve 321a over at least a time or more to form the curve changing point protruding in the width direction of the body 350, by which the turbulence activating part 321b is formed, and the second curved portion 322 that is formed opposite to the first curved portion 321 in the width direction thereof and is connected slowly to the first curved portion 321 to thereby form the curve closed face.
- the second curved portion 322 In the same manner as the first curved portion 321, the second curved portion
- the turbulence activating part 322b is formed.
- FIGS. 7 to 14 can be of course applied to the tube embodied in the heat exchanger using the carbon dioxide as the heat exchanging medium.
- a stress caused by the pressure of the carbon dioxide refrigerant more specifically, a stensile stress can be prevented from focusing on a certain part of the refrigerant passage 340.
- the resistant pressure strength is enough such that the carbon dioxide refrigerant can be substantially used as the heat exchanging medium.
- the shortest thickness t2 in the width direction of the body 350 of the thickness in the width direction between the inside passages 320 should be equal to or larger than the shortest thickness tl in the height direction of the body 350 of the thickness from the inner surface of each of the inside passages 320 to the outer surface of the body 350, which is set to satisfy the condition that t2 > tl .
- the shortest thickness t2 part in the width direction of the body 350 of the thickness in the width direction between the inside passages 320 is first broken off such that the inside passages 320 respectively function as a single passage. That is to say, the tube is deformed to a substantially cylindrical shape and after that, the shortest thickness tl part in the height direction of the body 350 of the thickness from the inner surface of each of the inside passages 320 to the outer surface of the body 350 is broken off. If the tube that satisfies the above condition t2 > tl is manufactured, it can be applied to the heat exchanger using the carbon oxide as replaceable refrigerant.
- the heat exchanger tube with a plurality of tumbling toy-shaped passages has the following advantages.
- the stress caused by the operating pressure of a heat exchanging medium can be evenly distributed onto the whole refrigerant passages, not gathered partially on the refrigerant passages, such that a resistant pressure strength is enough, thereby allowing the heat exchanging medium to be substantially replaced with carbon dioxide.
- the tube thickness can be maintained at a predetermined value, even when a hydraulic diameter is set low such that a heat transfer area is increased so as to improve the performance of a heat exchanger, thereby allowing the weight thereof and production cost to be reduced.
- the flux of the refrigerant can be increased by means of turbulence activating parts that face with each other in each of the refrigerant passages such that the thickness of the condensed liquid film can be substantially thin according to the acceleration of the turbulence of the refrigerant, thereby allowing a heat transfer efficiency to be enhanced.
- the refrigerant passing through the refrigerant passages is allowed activated to form the turbulence thereof since the turbulence activating parts face with each other in the width direction thereof, thereby allowing the heat transfer performance thereof to be improved.
- the forgoing embodiments are merely exemplary and are not to be construed as limiting the present invention.
- the present teachings can be readily applied to other types of apparatuses.
- the description of the present invention is intended to be illustrative, and not to limit the scope of the claims. Many alternatives, modifications, and variations will be apparent to those skilled in the art.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Geometry (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
KR20020005595 | 2002-01-31 | ||
KR2002005595 | 2002-01-31 | ||
PCT/KR2002/001217 WO2003064952A1 (en) | 2002-01-31 | 2002-06-26 | Heat exchanger tube with tumbling toy-shaped passages and heat exchanger using the same |
Publications (3)
Publication Number | Publication Date |
---|---|
EP1476709A1 true EP1476709A1 (en) | 2004-11-17 |
EP1476709A4 EP1476709A4 (en) | 2006-04-19 |
EP1476709B1 EP1476709B1 (en) | 2010-06-23 |
Family
ID=27607055
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP02741495A Expired - Lifetime EP1476709B1 (en) | 2002-01-31 | 2002-06-26 | Heat exchanger tube with tumbling toy-shaped passages and heat exchanger using the same |
Country Status (7)
Country | Link |
---|---|
US (1) | US6854512B2 (en) |
EP (1) | EP1476709B1 (en) |
JP (1) | JP3962798B2 (en) |
KR (1) | KR100906769B1 (en) |
CN (1) | CN100338425C (en) |
DE (1) | DE60236816D1 (en) |
WO (1) | WO2003064952A1 (en) |
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FR3101139B1 (en) * | 2019-09-24 | 2022-03-18 | Safran | HEAT EXCHANGER FOR TURBOMACHINE, TURBOMACHINE AND METHOD FOR MANUFACTURING THE EXCHANGER |
JP7496832B2 (en) * | 2019-10-10 | 2024-06-07 | 三菱電機株式会社 | HEAT EXCHANGER, HEAT EXCHANGER UNIT, REFRIGERATION CYCLE DEVICE, AND METHOD FOR MANUFACTURING HEAT EXCHANGE MEMBER |
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- 2002-06-25 KR KR1020020035530A patent/KR100906769B1/en active IP Right Grant
- 2002-06-26 WO PCT/KR2002/001217 patent/WO2003064952A1/en active Application Filing
- 2002-06-26 EP EP02741495A patent/EP1476709B1/en not_active Expired - Lifetime
- 2002-06-26 JP JP2003564505A patent/JP3962798B2/en not_active Expired - Fee Related
- 2002-06-26 DE DE60236816T patent/DE60236816D1/en not_active Expired - Lifetime
- 2002-06-26 CN CNB02827721XA patent/CN100338425C/en not_active Expired - Fee Related
- 2002-08-13 US US10/217,902 patent/US6854512B2/en not_active Expired - Lifetime
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US6289981B1 (en) * | 1997-05-30 | 2001-09-18 | Showa Denko K.K. | Multi-bored flat tube for use in a heat exchanger and heat exchanger including said tubes |
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Also Published As
Publication number | Publication date |
---|---|
KR20030065269A (en) | 2003-08-06 |
EP1476709B1 (en) | 2010-06-23 |
US20030141048A1 (en) | 2003-07-31 |
DE60236816D1 (en) | 2010-08-05 |
WO2003064952A1 (en) | 2003-08-07 |
JP3962798B2 (en) | 2007-08-22 |
EP1476709A4 (en) | 2006-04-19 |
KR100906769B1 (en) | 2009-07-10 |
JP2005516176A (en) | 2005-06-02 |
CN1618003A (en) | 2005-05-18 |
US6854512B2 (en) | 2005-02-15 |
CN100338425C (en) | 2007-09-19 |
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